Variable-speed gear.



No. 7l0,485. Patented on. 7, I902.

c. m. MANLY, VABIA'BLE- SPEED GEAR.

(Application filed Oct, 22,v 1901.) (No Model.)

4 Sheets-Sheet I.

Patented Oct. 7, I902.

C. M. MANLY.

VARIABLE SPEED GEAR.

(Application filed Oct. 22,1901.

4 Sheets-Sheet -2.

(No Model.)

No. 7l0,485.

Patentd Oct. 7, I902.

C. M.v MANLY. VARIABLE SPEED GEAR. App1ication filed 01.)

4 Sheets-Shed 3.

(No Model.)

Patented Oct. 7, I902.

C. M. MANLY.

VARIABLE SPEED GEAR.

(Application filed. Oct. 22, 1901.)

(No Model.)

THE "cams PETERS co. mm: \.|r w.. WASHINGTON, D.'c.

UNiTnn STATES PATENT OFFICE.

CHARLES M. MAN LY, OF IVASI'IINGTON, DISTRICT OF COLUMBIA.

i/ARiABLE-SPEED GEAR.

SPECIFICATION forming part of Letters Patent No. 710,485, dated October 7, 1902.

Application filed October 22. 1901- Serial No. 79,582- (No mOdQl) To all whom, it may concern:

Be it known that I, CHARLES M. MANLY, a citizen of the United States, residingat \Vashingtou, District of Columbia, have invented certain new and useful Improvements in Variable-Speed Gears, of which the following is a specification.

Hy invention relates to variable speedtransmitting mechanisms in which a pumping device and a motor operated by a fluid, preferably oil or water, delivered from the pump are interposed between a prime mover and a driven device, such fluid circulating through the pump and motor as a fluid connection.

My object is to provide simple and effective means in such mechanisms as that designated for varying at will the velocity ratio of the driven device to the prime mover from any predetermined positive value through zero to any other predetermined negative value, whereby the prime mover may be run at a constant speed and the driven device caused to operate at any desired speed between the maxim um speed in one direction, represented by the predetermined positive value, to a maximum speed in the reverse direction, rep resented by the predetermined negative value. My further object is to accomplish this desirable result in such a manner that any fluctuations in the velocity of the driven device relative to that oi the driving device or prime mover shall be so small at any speed as to be practically negligible; and, finally, my object is to provide a variable-speed gear of the character specified which shall be applicable to any situation where it is desirable or necessary to transmit varying speeds from a driving device to a driven device and which shall be especially adapted for use on motor-vehicles and other structures where the load or resistance varies within wide limits.

With these objects in view my invention consists of a speed-transmitting mechanism embodying a rotary reciprocating pump driven from any suitable external source of power, a rotary reciprocating motor connected to the pump by a fluid and adapted to be connected to a driven device, and means for adjusting the relative capacities of the pump and the motor, as hereinafter more particularly pointed out in the claims; and

my invention further consists in the novel construction and. details thereof with reference to the accompanying drawings, as hereinafter described, and more particularly pointed out in the claims.

In the drawings, which illustrate a preferred form in which my invention may be carried out, Figure 1 is a central longitudinal sectional view. Fig. 2 is a transverse sectional view taken on the line 2 2, Fig. 1, and looking in the direction of the arrows. Fig. 3 is transverse sectional view taken on the line 3 3, Fig. 1, looking in the direction of the arrows. Fig. 4 is a sectional plan view of the distributing-valve and relief-chamber, taken on the broken line 4 i, Fig. 1. Fig. 5 is an end elevation of the device for varying the capacity of the pump or the motor. Fig. 6 is a detached end elevation of the pump-cylinders viewed from a point between the motor and the pump. Fig. 7 is a detached plan view of the ureter-cylinders, and Fig. 8 is a diagrammatic view hereinafter referred to.

Referring now to the drawings, in which the same reference characters relate to the same or corresponding parts in all the views, the letter I indicates portions of a suitable fixed framework, in which is fixedly mounted a stationary valve E, provided with two semicircular poris P and P, consisting of cored passages extending through the valve struc ture and terminating in the inner faces of annular flanges projecting from the central web of the valve, said ports and constituent passages being separated from each other by narrow bridges or partitions G and G, diametrically disposed with reference to each other and here represented in a vertical plane, shown in Figs. 1 and 3. In order to strengthen the valve, I provide strengthening ribs or webs 1-1 H H 850., at suitable points, which ribs or webs, it will be understood, extend but a limited distance on either side of the central line of the valve and do not divide the ports. Upon opposite sides of the valve structure E, I arrange rotary-cylinder structures K and K having trnnnions forming outer bearings journaled, respectively, in bearings L and L carried by the frame I, and inner bearings journaled, respectively, in bushings L L',, carried by the valve structure.

In the drawings I have shown the pump structure on the left of the valve and the motor structure on the right, and as the construction of both is similar a detailed description of one-for example, the pump-will be sufficient to clearly set forth the manner in which both are to be made, these two elements of the device differing from each other only in the functions performed, which will be defined at the proper places in this specification.

The rotary-cylinder structure of the pump is provided with a plurality of cylindrical chambers A A A A A A constituting the radial pump-cylinders, which cylinders may be formed in the rotary-cylinder casting, or in any suitable manner and are radially disposed around the axial line act of the structure, such axial line passing centrally through the valve structure and the trunnion-bearings of the pump and motor structures. The cylinders A A A the. are provided with suitable ports p, p, 19 19 p, and p adapted to register successively with the ports P and P during the rotation of the pump structure. Pistons B, B, B B B and B are slidably mounted in the cylinders and are connected to a relatively fixed but radially-adjustable crank-pin C by means of connecting-rods D, D, D D D", and D having a rocking connection with the pistons and adapted to turn on and around the crank-pin.

The cylinder structure K is adapted to be rotated in its bearings by suitable driving connections with a prime moveras, for example, by means of a sprocket S, fixed to the cylinder structure and driven by suitable connections with said prime mover.

The crank-pin O in the position shown in the drawings, Figs. 1 and 2, is eccentrically disposed with reference to the central axial line a a and is carried by a shaft N, mounted in the eccentric bore of a bush M, the outer or peripheral surface of which is concentric with respect to the trunnion-bearing of the cylinder structure K, in which trunnion said bush is rotatably mounted.

The bush M is fixed, by means of a suitable key or other fastening means, to a worm-gear Q, and the shaft N is similarly fixed to a spurgear T, operating as an inner gear, meshing with internal teeth R on a worm-gear O, rotatably mounted upon the exterior surface of the bush M.

The eccentricity of the bore in the bush M is preferably made equal to the eccentricity of the crank-pin O with reference to its shaft N, because when such is the case the crankpin C may be caused to move radially in a straight line toward and through the central axis a.- ct by such proper relative motions of the shaft N and the bush M in opposite directions as will give to the bush M one-half the angular displacement around the central line a a and referred to a fixed diameter of the valve E that is given to the shaft N around its central line Z) I) and referred to the line connecting the center of said bush M and the center of said shaft N.

By reference to Figs. 5 and 8 it will be seen, therefore, that when the length of stroke of the pistons is changed by this radial adjustment of the crank-pin O the angular position of the crank-pin C with respect to the valve E, Whose axial line is on the center line a a, will not be changed and hence the ports in the cylinder structure will always arrive at their proper positions with respect to the ports in the valve at the proper time in their cycle. In order to eifect this adjustment of the crank pin 0, so that the resultant motion of the said pin due to the rotation of the bush M and the shaft N in opposite directions shall be in a straight line, it is evident that the bush M must be rotated at such a speed with respect to the speed of rotation of the shaft N that the angulardisplacement of said bush around the center line a a and referred to a fixed diameter of the valve E shall always be onehalf the angular displacement of the shaft N in the opposite direction around its center line b b and referred to the line connecting the center of the bush M to the center of the shaft N.

In order to effect the rotation of the bush M and the shaft N in opposite directions and at their proper relative rates, any suitable means may be employed, and I have indicated, with the relative proportions of the parts as shown, one convenient means consisting of two worm-screws 4V and Y, meshing with their respective worm-wheels O and Q, said worms being connected together through two meshing spur-wheels 0 and q,.

mounted upon their respective worm-shafts and driven by any suitable means, and in order to give to the bush M its angular displacement around the axis a a and referred to 'a fixed diameter of the valve E of one-half the angular displacement of the shaft N around its central line b b and referred to the line connecting the center of the bush M to the center of the shaft N the ratio of the diameter of the spur-wheel o to the diameter of the spur-wheel q may be made equal to the ratio of the diameter of the internal gear R to the diameter of the spur-gear T, provided the diameters of the worm wheels 0 and Q are equal and also the pitches of the wormscrews W and Y are equal.

Referring to Figs. and 8, it will, however, be seen that the amount of motion which must be imparted to the inner gear T by the rotation of the Worm-wheel O is entirely dependent on the relative diameters of the inner gear T and the internal gear R, since the inner gear T will be half the diameter of the internal gear R when the pitch diameter of the inner gear T is equal to twice the eccentricity of bore of the bushM, and in this case the worm-Wheel 0 would not need to be moved at all in order to effect the radial adjustment of the crank-pin, since the gear T would receive all of its requisite motion throughits IIO being rotated around the center Z) l) by its teeth meshing with the teeth of the internal gear R as the bush M is rotated. Furthermore, it will be seen that should it be desired to make the diameter of theinner gear T less than twice the eccentricity of bore of the bush M it would be necessary to impart to the gear T through the medium of the internal gear R, carried by the worm O, a slight rotation in the same direction as the rotation of the bush M in order to compensate for the excess of rotation which the inner gear T would receive from the internal gear B through the rotation of the bush M, and thus it is seen that the relative proportions of the inner gear T and the internal gear R determine at once both the amount and direction of rotation which must be imparted to the gear T by the worm TV.

In Fig. 8 the full lines represent the first relative positions of the crank-pin C, shaft N, and bush M, while the dotted lines represent three separate relative positions of the several parts, the single dotted line indicating the first position, the double dotted line the second position, and the triple dotted line the third position, from which it is evident that the angular displacement of the shaft N around its central line Z) I) and referred to the line joining the center of the bush M to the center of the shaft N of twice the angular displacement of the bush M around its central line (L a and referred to a fixed diameter of the valve E will preserve the same angular relation of the crank-pin C on the shaftN with respect to the valve E. Furthermore, it will be seen that the length of stroke of the pistons B B B B 850., may be varied from maximum to nil by rotating the shaft N around its central line b I) through one hundred and eighty degrees, and during such movement to obviate any angular displacements of the crank-pin G with respect to the valveE atintermediate points the said crankpin 0 must move radially from the maximum to the position where the stroke is ml, which result is effected, as hereinbefore indicated, by rotating the bush M at the proper rate of speed in the opposite direction with respect to the rotation of the shaft N. The several cylinders A A A 50., are provided with corre sponding ports 23 1) P 850., adapted to register successively with the ports P and P in the valve structure,as hereinbefore indicated, so that when the cylinder structure is rotated, for example, in a direction as indicated by the arrow, Fig. 2, the upper cylinder A being at its upper dead-center, the lower cylinder A being at its lower dead-center, the ports of the cylinders A A and A will first register with the port P in the valve, and as the pis tons are making the inward stroke said port P will act as an inlet-port to supply the said cylinders with fluid as the pistons respectively perform their suction-strokes, the cylinders-A A and A following in succession. On the other hand, the ports of the cylinders A A and A will first register with the port P of the valve structure, and as the pistons during that part of the rotation of the cylinder structure are making their outstroke or delivery-stroke the fluid contained in the cylinders will be forced outwardly through their ports into the port P of the valve structure, the cylinders A, A and A following in succession.

To prevent intercommunication between the pressure and suction ports of the valve E as the cylinder-ports pass the bridges, the bridges G and G are made equal in width to the width of the cylinder-ports p, the. The rotation, therefore, of the rotarycylinder structure on the left side of the valve structure causes the several pistons to operate as a hydraulic pump, fluid being drawn into one half of the cylinders while fluid is being forced out by the other half through the receiving and distributing ports of the said valve, and in order to cause said fluid to be circulated in a closed circuit and constitute a fluid or liquid connection between the driving element of a power-transmitting device connected to a prime mover and the driven element thereof I provide for the utilization of the delivery from the pump as a means for operating a motor independently movable with respect to the pump structure and connected to the driven part or device, so that the connection between the pump and said motor may be varied in such a Way as to vary the relative speeds of the two elements of the transmitting device, and I preferably effect this object by means of a plurality of cylinders A, A A A &c., mounted on a cylinder structure K,, here shown as similar in all respects to the cylinder pump structure and having trunnion-bearings journaled at the outer end in a sleeve L,, secured in the frame I, and at the inner end in the bush or sleeve L,, mounted in the valve structure E.

The motor-cylinder structure is here indicated as similar to the pump-cylinder structure, and each cylinder has a corresponding reciprocating piston 13,13 B 850., connected by corresponding piston-rods D, D 850., to a crank-pin 0,, carried byashaft N,, mounted in an eccentric bore of the bush M,, said crank-pin C, being relatively fixed and located with reference to the axis of the shaft N, a distance equal to the eccentricity of the bore of the bush M the latter of which has a concentric bearing-surface confined to a concentric internal bore of the trunnion in the cylinder structure.

The crank-pin G, of the motor structure is relatively fixed, but adjustable, and is here Shown as located at a point below the center line a a, and one hundred and eighty degrees from the crank-pin O, and the cylinders are provided with ports 19, 19 the, adapted to suecessively register with the ports P and P in the valve structure E, and said valve structure is-so disposed that as one-half of the pump-cylinders is delivering fluid thereto one-half of the motor-cylinders is receiving the fluid so delivered, thereby giving the corresponding pistons in said motor-cylinders their inward stroke, and as the crank-pin C, is relatively fixed the pressure between the respective pistons and the heads of the motor-cylinders will cause said motor-cylinder structure to rotate in the same direction as the pump-cylinder structure, and while the other half of the pump-cylinders is drawing in fluid from the distributing-port P of the valve structure the other half of the motorcylinder structure is exhausting fluid into said port, and thus a fluid connection may be maintained between the pump and the motor structures.

The relatively fixed crank-pin O is similarly located with respect to its shaft N and the eccentricity of the bore of the bush M is likewise similarly disposed with reference to the eccentricity of the crank-pin O, as in the pump structure, while the worm-wheels Q and 0 and the inner gear T are all similarly connected to their respective parts, so that the crank-pin 0 may be adjusted in a radial line with respect to the face of the valve structure E in exactly the same way as the crank-pin O of the pump structure.

The interior space of the valve structure and the cylinder structure and the passages between the rotary-cylinder pump structure and the rotary-cylinder motor structure are intended to be supplied with fluid, preferably oil or water, in order to provide the fluid connection heretofore referred to, and whenever in the operation of the device there should be any deficit of fluid in the cylinders of either the pump or motor structures such deficit may be made up from the internal space of the structures, which acts as a res ervoir, through the medium of spring-closed valves 11 o, &c., and '21, 11 850., located in the heads of their respective pistons and opening outwardly toward the outer heads of the cylinders.

Referring to Figs. 1 and 4, it will be seen that I have provided means for relieving the fluid connection of any excess fluid which at any time may exist in it-due to any cause, such as a change in the capacities of either the pump-cylinders or the motor-cylinders, consisting of a relief-chamber d, mounted on the exterior of the valve structure E, said relief-chamber 61 being connected to the ports P and P, respectively, through the passages t and t, said passages 15 and 15, respectively, opening into the relief-chamber d through the ports 8 and s. This relief-chamber is bored to receive a piston-valve V, composed of a stem connecting two pistons h and h and adapted to move back and forth in the bore of said relief-chamber, but which is limited in its extent of motion by the stops it a, formed on the inner ends of the plugs 'r 1", closing the bore of said relief-chamber d. On that side of the relief-chamber (1 next to the valve structure E are formed channels c and e, while the relief chamber is also connected through the portfto a passage g in the bridge G of the valve structure E, said. passage 9 continuing from the bridge G down through the web of the valve structure E to the central space of the rotary-cylinder structures. To accomplish the relief of any excess of fluid in the suction-port of the valve E, and at the same time to retain the pressure in the pressure-port of the valve structure E, the distance between the two piston-heads h h and the length of the stops it and u on the plugs r and r are such that when one headsay hof the-valve V covers the inner end of the channel the other head it of the valve V will rest in the position shown, thus allowing any excess of fluid which might be in the port P to pass out through the port' 3, the channel 6, the port f, and the passage g into the central space of the rotary-cylinder structures, while the fluid which is under pressure in the port P of the valve E will pass into the other end of the relief-chamberd, but striking against the head h of the piston-valve V will keep said piston-valve forced against the projection u of the plug T, which in turn will cause the head 72- to close the inner end of the channel 2, which, as is readily seen, will prevent any direct communication between the pressureport of the valve E and the interior of the drum, except in the proper way. It will thus be seen that the piston valve V normally closes the pressure or de-' livery port of the valve E from the central space and normally opens the suction-port thereof to said central space. Similarly it will be seen that should the pressure on the head 71 be greater than the pressure on the head 77. of the piston-valve V said piston-valve will be forced over against the projection uof the plug 7', which will permit the port P to communicate through the channel e, the port f, and the passage 1 with the central space of the rotary-cylinder structures, but will shut off communication between the port P of the valve E and said central space. Such an automatic change, however, in the position of the valve V can only occur when the ports P and I change functions, and thus this change in the position of the pistonvalve V automatically relieves any excess of fluid occurring in the suction-port of th valve E.

It should be observed that the port f is made slightly less in cross-sectional area than the ports 8 or s, so that the pressure of the fluid passing through the ports 8 or s at the proper times will accumulate behind that piston-head which is in contactwith its stop, and thus readily effect the automatic shifting of the piston-valve V from one side to the other.

From the foregoing description of the valve V and its cooperating parts it will be seen that said supplementary valve controls passages which connect the ports of the main valve with the central space or reservoir, so

that not only will said valve act to relieve excess of fluid between the pump and motor, but it may also act to supply any deficit that may occur in the fluid connection between said pump and motor, by which means the required quantity of fluid between the pump and motor may always be insured. \Vhen, therefore, the supplementary valve V is utilized to supply deficit of fuel to the fluid connection between the pump and motor, as above described, it is evident that the reservoir (here shown as the central space) may be located at any convenient point.

The operation of the device is as follows: Suppose the parts to be in the position shown in Fig. l, where the crank-pin O of the pump is at its point of maxim um throw, the cylinder A at its upper dead-center, the cylinder A at its lower dead-center, and the other cylinders occupying relative positions around the crank-pin corresponding with their angular displacements around their common axis of rotation and the corresponding motor-cylinders in their relative positions around the axis (t a, the cylinder A being at its lower dead-center. The interior of the cylinder structures, including the central space, and all the passages having been supplied with oil or water the pump-cylinder structure is rotated through the medium of the sprocket S, driven from a prime mover, by which operation the pistons are caused to reciprocate in the pum p-cylinders as the said pistons are carried around the crank-pin C, thus acting upon the fluid in the cylinders to force the same through the respective cylinder-portsp p 13 the, into the port P in one half of the valve and to suck fluid from the port P in the other half of the valve and from the interior space of the cylinder structure. As the direction of rotation of the pump-cylinders is fixed, the radial position of the crank-pin C will determine the function of the ports P and P as delivery or pressure port and inlet or suction port, since these ports change functions as the crank pin C in its adjustments is passed through the axial line a a. If the pump-0y linder structure is rotated in the direction of the arrow, Fig. 2, it is evident that as the cylinders rotate successively from the position occupied by A the relative motion of the pistons with respect to the cylinder-heads will be away from the said heads, thus constitut ing the suetiomstrokes of the pump-cylinders, which continue until the cylinders have passed through one hundred and eighty degrees, during which movement fluid is drawn into the cylinders from the port P and from the interior spaces. After passing through onehundred and eighty degrees from the position of cylinder A the cylinders in completing the cycle through the remaining one hundred and eighty degrees become forcing-pumps, because the relative motion of the pistons with respect to the cylinderheads is toward said cylinder-heads, thereby forcing the fluid out of the cylinders through the ports p 1)" p 850., into and through the port P. Such action of the pump-cylinders, since they are connected with the motor-cylinders A A A &c., through their ports and the valve-ports, causes a circulation of the fluid from The pump-cylinders through the port P to the motor-cylinders and through the port P back to the pumpt-ylinders, thus establishingaclosed fluid connection or circuit between the pump and the motor, and hence the motor-pistons will be caused to reciprocate with respect to their cylinders in succession, thereby rotating the motor-cylinder structure in the same direction as the pump-cylinder structure. As the fluid is delivered to the motor-cylinders at the same rate as it is discharged from the pump-cylinders and is exhausted from the motor at the same rate that it enters the pumpcylinders, it is obvious that in the position shown and with the pump and motor cylinders of the same capacity the motion imparted to the motor-cylinders by the fluidpressure from the pump will be the same as that of the pump and may be delivered by a suitabledrivingconnection,such asasprocket 8,, to any-device. If it is desired to vary the speed of the motor-cylinder structure, so as to vary the speed of the driven device, the position of the crank-pin C may be altered. To accomplish this, suppose the hush M to be given an angular movement in either direction and att-he same time the shaftN be given an angular movement around its center I) b, but in a reverse direction, in the the manner hereinbefore indicated, the throw of the crank-pin G will he steadily decreased, depending in amount on the extent of the angular movements of M and N, but the center of the crank-pin C will at all times remain in the same plane, passing through some predetermined point of the bridge G or of the bridge G and the axis a a. Upon thus decreasing the throw of the crank-pin C the amount of fluid forced by the pump into the port P will be correspondingly decreased, which decrease will in turn cause the motorcylinders A A A A A &c., and consequently the driven device, to revolve ata de creased rate. If the angular movement of the bush M around its axis a a be continued through ninety degrees from its original position, as shown in Fig. 1, and the angular movement of the shaft N around its center line b b at the same time be continued at its proper rate and in the direction reverse to that of M with respect to the center line or axis a a, the crank-pin C will then be in a position where it will have no throw, when of course the pump will do no work, and this will cause no pressure to be exerted on the fluid, and there will consequently be no tendency to rotate the motor-cylinders A A A A A &c., and thus there will be no power delivered to the driven device. If the angular rotations of the bush M and the shaft N be continued still farther in the directions given above and at their respective rates, the crankpin 0 will continue in its plane, as above, from the position of no stroke to a lower position, at which the amount of stroke will depend on the extent of angular motions given to the bush M and shaft N. However, as soon as the crank-pin C has passed the position of no stroke to a lower position the pump-cylinders A, A, A A A and A immediately begin to pump; but the port P of the valve E, which in the description above was the pressure-port, nowbecomes the suction-port, while the port P becomes the pressure-port, the piston-valve V of the relief-chamber automatically cutting off communication between the port P and the central space and establishing communication between the port P and said central space, and this change causes the motor-cylinders A A A A A &c., to revolve in a direction opposite to that in which they revolved when the crank-pin O was above the center line a a of Fig. l, and thus it will be readily seen that by similaradjustments of the crankpin 0 below the axis a a the motor-cylinders may be given within the predetermined limits of the device any speed which may be desired in this opposite direction.

The above description of the device is based on the supposition that the crank-pin C of the motor remained in the position itis shown in Fig. l, which is its maximum radial adjustment. In this position of the crank-pin C the motor-cylinders exert their maximum torque. Now suppose the driven device while requiring a slow speed also requires very little torque it will be seen that by adjusting the crank-pin C of the pump nearer to its position of no stroke than would be required to give the desired speed to the driven device when the crank-pin 0 had its maximum adjustment from the center line a a we may by also radially adjusting this motor crank-pin O nearer to the center line or axis a a by its device similar to that employed for radially adjusting the pump crank-pin G obtain the desired speed and torque and at the same time obviate any excessive travel of the pistons in their respective cylinders. It is also apparent that by having the crank-pin of the pump and the crank-pin of the motor both adjustable it is possible to secure a greater range of velocity ratio between the motor and the pump, and consequently between the driven device and the prime mover, than if they were not both adjustable.

It is also possible to use my device as a brake when slowing down or when the driven device would continue to revolve from power furnished from another source. For example, were it attached between the prime mover and the wheels of a vehicle in motion the inertia of the vehicle could be utilized to drive the prime mover at any speed desired and in either direct-ion by a proper relative adjustfinitely small amounts and the direction of the driven device reversed and its velocity ratio in such reverse direction increased by infinitely small amounts from ml to maximum, and vice versa. Furthermore, my construction, with such wide range of variations in the relativespeeds of the prime mover or driving device and the driven device is such that the various changes of speed through reversal and maximum in the reverse direction may be effected by the simplest movements of the controlling device, such as a handwheel under the control of the driver or operator, for it is obvious that such controlling device need be moved in one direction only to effect the various changes incident to the change from a predetermined positive value to a predeterminednegative value.

While I have shown six cylinders in the pump and motor, it will be understood that a greater or less number may be used, if desired, and that the number ofcylinders of the pump may be greater or less than the number of cylinders of the motorwithout departing from the scope of my invention, and it is to be further understood that the normal capacity of the pump or motor cylinders may be either the same or different and that the individual cylinders may be of the same or different normal capacities, according to the nature of the device to which my invention is applied.

It will of course be understood that wherever necessary the joints will be suitably packed by any of the means well known to the art.

I claim as my invention-- 1. A variable-speed gear comprising a driving element, consisting of arotary radial cylinder-pump, the cylinder structure of which is adapted to be connected to a driving device, a driven element, consisting of a rotary radial cylinder-motor, the cylinder structure of which is adapted to be connected to a driven device, a fluid connection between the pump and motor, and means for varying the capacity of the pump.

2. A variable-speed gear comprisinga driving element, consisting of a rotary-cylinder structure adapted to be connected with a driving device and havinga plurality of radial cylinders and cooperating pistons therein acting as a pump, a driven element, consisting of a rotary-cylinder structure adapted to be connected to a driven device and having a plurality of radial cylinders and cooperating pistons therein acting as a motor, a fluid connection between the pump and motor, and means for altering the relative capacities of the pump and motor.

3. A variable-speed gear comprising a driving element, consisting of a rotary radial-cylinder pump, the cylinder structure of which is adapted to be connected toadriving device, a driven element, consisting of a rotary radialcylinder motor the cylinder structu re of which is adapted to be connected toadriven device, a fluid connection between the pump and motor and means for altering the relative capacities of the pump and motor and adapted to change the direction of rotation of the motor.

t. A variable-speed gear com prising a d riving element, consisting of a rotary radial-cylinder pump, the cylinder structure of which is adapted to be connected to a driving device, a driven element consisting of a rotary radialcylinder motor,thecylinderst ructure of which is adapted to be connected toadriven device, a fluid connection between the pump and motor, and means for varying the capacity of the motor, substantially as described.

5. A variable-speed gear comprisinga driving element, consisting of a rotary-cylinder structure adapted to be connected to a driving device and having a plurality of radial cylinders therein and cooperating pistons acting as a pump, a driven element, consisting of a motor similarly constructed, the cylinder structu re of which is adapted to be connected to a driven device, a valve interposed between the pump and motor, said valve having ports through which the pump and motor may be connected by a fluid, and means for varying the relative capacities of the motor and pump.

6. A variable-speed gearcomprisinga driving element consisting of a rotary-cylinder structure having a plurality of cylinders therein, cooperating pistons in said cylinders acting as a pump, a relatively fixed crank-pin eccentrically disposed with reference to the axis of the cylinder structure and connected to the pistons, a driven element consisting oi a rotary-cylinder structure having cylinders and pistons and cooperating elements acting as a motor, a fluid connecting the pump and motor, and means for adjusting either ot'said crank-pins, whereby the relative capacities of the pump and motor maybe varied, substantially as described.

7. A variable-speed gear comprising a driving element consisting of a rotary-cylinder structure having a plurality of cylinders therein and pistons in said cylinders, acting as apump, a relatively fixed crank-pin, and rods connecting the pistons with said pin, a driven element consisting of a rotary-cylinder structure having a plurality of cylinders therein and pistons in said cylinders, acting as a motor, a crank-pin to which said pistons are connected, a valve interposed between the pump and motor having ports through which a fluid passes to connect the pump and motor, and

means for adjusting one of the crank-pins, whereby the relative capacities of the pump and motor may be varied, substantially asdescribed.

R. A variable-speed gear comprisi ng a driving element consisting of a rotary-cylinder structure having a plurality of cylinders therein, pistons in said cylinders, acting as a pump, a relatively fixed crank-pin, and rods connecting the pistons with said pin, a driven element consisting of a rotary-cylinder structure having a plurality of cylinders therein and pistons in said cylinders, acting as a motor, a crank-pin to which said pistons are connected, a stationary valve interposed between the pump and motor having ports through which a fluid passes to connect the pump and motor, and means for adjusting one of the crank-pins, whereby the relative capacities of the pump and motor may be varied, substantially as described.

9. Avariable-speed gear com prising a driving element consisting of a rotary-cylinder structure having a plurality of cylinders therein, pistons in said cylinders, acting as a pump, a relatively fixed crank-pin, and rods connecting the pistons with said pin, a driven element consisting of a rotary-cylinder structure having a plurality of cylinders therein and pistons in said cylinders, acting as a motor, a crank-pin to which said pistons are connected, a stationary valve interposed between the pump and motor having ports through which a fluid passes to connect the pump and motor, and means for moving one of the crank-pins diametrically of the valve, substantially as described.

10. In a variable-speed gear, the combination of a rotary-cylinder pump structure having a plurality of cylinders and cooperating pistons therein, a crank-pin to which the pistons are connected, a rotary-cylinder motor structure comprising corresponding elements to the pump structure, a stationary valve interposed between the pump and motor structures, having ports through which a fluid may pass to connectthe pump and motor, and means for adjusting the crank-pins in a straight line parallel with a diametrical line of the valve, substantially as described.

11. In a variable-speed gear, the combination of a rotary-cylinder pump structure having a plurality of cylinders and cooperating pistons therein, a crank-pin connected to said pistons, a rotary -cylinder motor structure having a plurality of cylinders and cooperating pistons therein, a crank-pin connected to said pistons, a valve having ports therein interposed between the pump and motor structures, through which a fluid may pass to connect the pump and motor, and means for adjusting the crank-pins of the motor and pump in a straight line parallel to a diametrical line of the valve, substantially as described.

12. In a variable-speed gear, the combination with a driving element consisting of a rotary reciprocating piston pump the cylinder structure of which is adapted to be connected to a driving device, a driven element consisting of a rotary reciprocating piston motor the cylinder structure of which is adapted to be connected to a driven device, a crank-pin for each to which the pistons are connected, a fluid connection between the pump and motor, a bush rotatably mounted in a bearing concentric with the common axis of rotation of the pump and motor and having an eccentric bore, a shaft, by which the crankpin is carried, rotatably mounted in said eccentric bore, the eccentricity of the crank-pin being equal to the eccentricity of the bore of the bush with reference to the said axes of rotation, and means for rotating the bush and the shaft in opposite directions, substantially as described.

13. In a variable-speed gear, the combination with a driving element consisting of a rotary reciprocating piston pump the cylinder structure of which is adapted to be connected to a driving device, a driven element consisting of a rotary reciprocating piston motor the cylinder structure of which is adapted to be connected to a driven device, a crank-pin for each to which the pistons are connected, a fluid connection between the pump and motor, a bush rotatably mounted in a bearing concentric with the common axis of rotation of the pump and motor and having an eccentric bore, a shaft, by which the crank-pin is carried, rotatably mounted in said eccentric bore, the eccentricity of the crank-pin being equal to the eccentricity of the bore of the bush with reference to the said axes of rotation, and means for rotating the bush and the shaft simnltaneouslyin opposite directions, substantially as described.

1%. A variable-speed gear comprising a rotary-cylinder pump structure adapted to be connected to a driving device and having a plurality of radial cylinders and cooperating pistons, a rotary-cylinder motor structure adapted to be connected to a driven device and having a plurality of radial cylinders and cooperating pistons, a fluid connecting the pump and the motor, and means for independently altering the capacities of the pump and the motor, substantially as described.

15. In a variable-speed gear having a rotarycylinder structure, with cylinders and cooperating pistons therein, a crank-pin to which the pistons are connected, a bush having an eccentric bore rotatably mounted in a hearing concentric with the axis of rotation of the rotary-cylinder structure,a shaft, by which the crank-pin is carried, rotatably mounted in said bore, of the bush, and means for simultaneously rotating the bush and the shaft in opposite directions and adapted to cause the crank-pin to move in a straight line, substantially as described.

16. In a variable-speed gear having a rotarycylinder structure, with cylinders and cooperating pistons therein, a crank-pin to which the pistons are connected, a bush having an eccentric bore rotatably mounted in a bearing concentric with the axis of rotation of the rotary-cylinder structure, a shaft, by which the crank-pin is carried, rotatably mounted in said bore of the bush, the eccentricity of the bore and the crankpin being equal, and means for rotating said bush around its center in the opposite direction and at one-half the rate that the shaft is rotated around in the eccentric bore of said bush, substantially as described.

17. In a variable-speed gear, thecombination of a rotary radial-cylinder pump the cylinder structure of which is connected with a driving device, a rotary radial-cylinder motor connected with a driven device, a fluid between said pump and motor, and a space between the pump and motor structures supplied with fluid, a valve interposed between the pump and motor provided with ports which act as delivery and suction ports of the pump, and means for relieving any excess of fluid, substantially as described.

18. In a variable-speed gear, the combination of a pump connected with adriving device, a motor connected with a driven device, a fluid between the pump and motor, and a space between the pum p and motor structures supplied with fluid, a valve interposed between the pump and motor and provided with ports which act as delivery and suction ports of the pump, and a supplementary valve controlling passages between the central space of the pump and motor structures and the suction-port of the valve, whereby excess of fluid is relieved by directing such fluid excess through the supplementary valve into the central space of the pump and motor structures, substantially as described.

19. In a variable-speed gear, the combination of a rotary-cylinderpump structure, connected with a driving device, a rotary-cylinder motor structure connected with a driven device, a space between the. pump and motor structures, a valve interposed between the pump and motor structures and provided with ports connecting the pump and the motor structures, a supplementary-valve chamber connected by ports and passages with the space between the pump and motor structures and with the ports of the valve between the pump and motor, and a valve in said chamber adapted to control the ports and passages of the supple mentary-valve chamber, so as to relieve excess of fluid in the suction-port of the valve structure, substantially as described.

20. In a variable-speed gear, the combination of a rotary-cylinder pump structure connected with a driving device, a rotary-cylinder motor structure connected with a driven device, a space between the pump and motor structures supplied with fluid, a main valve interposed between the pump and the motor structures and provided with ports acting as suction and delivery ports of the valve, means for causing the ports of the main valve to change their functions and reverse the direction of rotation of the motor structure, a supplementary-valve chamber, and a valve therein, controlling passages and ports connecting the space between the pump and motor structures with the suction-port of the main valve, and means for causing said supplementary valve to automatically shift when the suctionport in the main valve changes function, substantially as described.

21. In a variable-speed gear, the combination of a rotary-cylinder pump structure connected with a driving device, a rotary-cylinder motor structure connected with a driven device, a space between the pump and motor structures supplied with fluid, a main valve interposed between the pump and motor'structures and provided with ports acting as delivery and suction ports of the pump and controlling the passing of a fluid between the pump and motor, a supplementary valve chamber connected by ports and passages with the space between the pump and motor and with the ports of the main valve, and a valve in said chamber normally closing the port leading to the passage connected with the delivery-port of the main valve and opening the port leading to the passage connected Let r" C o "T3 with the suction-port of said main valve, means for causing the ports of the main Valve to change functions, and means for automatically shifting the supplementary valve when the functions of said main-valve ports are changed, substantially as described.

22. In a variable-speed gear, the combination of a pump connected with a driving device, a motor connected with a driven device, a relatively fixed valve interposed between the pump and motor, and provided with ports which act as delivery and suction ports of the pump and through which ports a fluid may pass to connect the pump and motor, a reservoir for the fiuid connected by passages with the ports of said valve, and a supplementary valve controlling said passages and adapted to insure the required quantity of fluid between the pump and motor, substantially as described.

In testimony whereof I have signed my name to this specification in the presence of two subscribing witnesses.

CHARLES M. MANLY.

\Vitnesses:

O. W. FOWLER, R. T. FRAZIER.

It is hereby certified that in Letters Patent No. 710,485, granted October 7, 1902, upon the application of Charles M. Manly, of Washington, D. 0., for an improvement in Variable-Speed Gear, an error appears in the printed specification requiring correction, as follows: In line 9, page 5, the Word fuel should read fluid; and that laifiili No. 710,485

the said Letters Patent should be read with this correction therein that the same may l l conform to the record of the case in the Patent Office. Signed and sealed this lth day of November, A. 1)., 1902.

[sEAn] F. I. ALLEN,

Commissioner of Patents. 

